Roller with axial travel

ABSTRACT

The invention relates to a distributing roller with axial travel, comprising a gear that is located in the interior of the roller for generating a speed which differs from that of the roller sleeve. Said roller has means consisting of a bearing that is positioned obliquely in relation to the rotational axis for generating the axial travel.

[0001] The invention relates to a roller in accordance with the preambles of claims 1 and 11.

[0002] A roller with means for the axial movement of the roller shell is known from EP 0 607 283 B1, wherein a rotary movement is converted into an axial lift movement. This takes place in that a difference in the number of revolutions is created between the roller and cylindrical elements located in the roller interior by means of a gear, so that a lifting movement of the roller shell is generated by using a cam unit.

[0003] DE 39 35 422 A1 discloses a coupling with coupling halves which are arranged eccentrically in relation to each other.

[0004] DE 32 41 863 C1 discloses a jack hammer with a rotating tumbler disk.

[0005] The object of the invention is based on developing a roller.

[0006] In accordance with the invention, this object is attained by means of the characteristics of claims 1 and 11.

[0007] The advantages which can be achieved by means of the invention reside in particular in that a compact structural unit was created, which can be installed without problems in rollers with larger roller diameters, as well as in rollers with lesser roller diameters. The length of the roller lift can be set.

[0008] High manufacturing costs are avoided by using simple components, such as roller bearings or ball and socket joints.

[0009] An exemplary embodiment of the invention is represented in the drawings and will be described in greater detail in what follows.

[0010] Shown are in:

[0011]FIG. 1, a longitudinal section through one end of the friction roller in accordance with the invention,

[0012]FIG. 2, a portion of the representation in FIG. 1 with a setting of the lift length of the friction roller which differs from FIG. 1,

[0013]FIG. 3, a greatly simplified representation of a section III-III in FIG. 1 in a first operating position, as well as in a second one, shown in dashed lines, of the two-part coupling.

[0014] A roller 01, for example a friction roller 01 of an ink unit of a rotary printing press, consists of a roller shell 02, which is closed off on each of two sides with a ring-shaped flange 03. Each flange 03 receives in its central bore 04 a shaft 06, which is seated fixed on a lateral frame, as well as fixed against relative rotation. A bearing, for example a rolling bearing 07, is located between the shaft 06 and the bore 04, which can be displaced on its inner race 08 in the axial lift direction A by a defined amount, for example an axial lift length h.

[0015] A gear 09, which has a first gear wheel 13 with an axis of rotation 24, is rotatably seated on the shaft 06 by means of bearings, for example roller bearings 11, as well as seated eccentrically by an amount e in respect to the axis of rotation 12 of the friction roller 01. An exterior tooth arrangement 14 of the gear wheel 13 is in engagement with a second gear wheel 18 of the gear 09, is fixedly arranged on the interior 16 of the roller, shell 02 and has an interior tooth arrangement 17. The first gear wheel 13 has approximately 0.9 times the number of teeth of the second gear wheel 18.

[0016] On its flank facing away from the flange, the first gear wheel 13 has two, but preferably several, for example four catches, which project out of the flank in the axial direction and are spaced apart, for example stud bolts 20, 21, 22, 23. The stud bolts 20 to 23 constitute a first portion of a two-part coupling 26. They interlockingly enter into bores 27 to 30 of a second part of the coupling 26, which is rotatably seated on the shaft 06. The second part of the coupling 26 consists of a drive element 33, seated by means of bearings, for example roller bearings 32, on the shaft 06 as the support of an inner race 34 of a rolling bearing, for example a roller bearing 36.

[0017] An axis of rotation 37 of the roller bearing 36 extends at an acute angle α of 5° to 15° in respect to the axis of rotation 12 of the friction roller 01. The obliquely arranged roller bearing 36 is used as a lift gear for generating the axial lift of the friction roller 01. This is generated in that an outer race 38 of the roller bearing 36 is interlockingly connected via a joint 39 with the interior 16 of the roller shell 02.

[0018] The joint 39 consists of a connecting rod 41, each of whose ends 42, 43 is embodied as a joint 44, 46.

[0019] The first ball and socket joint 44 arranged on the outer race 38 of the ball bearing 36 is arranged so that it can be pushed back and forth via its ball socket in the direction of the axis of rotation 37 of the ball bearing 36 (FIG. 2). This can take place in that a side of the first joint 44 close to the outer race can be displaced by means of guide beads in radially extending grooves of the outer race 38 and arrestably in active contact—not represented in the drawings.

[0020] By means of this measure it is possible to change the lift length h represented in FIG. 1, in particular to shorten it in accordance with FIG. 2.

[0021] The diameter D of each bore 27 to 30 corresponds at least to the diameter d of each stud bolt 20 to 23, plus twice the amount e of the eccentricity of a section 47 of the shaft 06.

[0022] The friction roller 01 operates as follows:

[0023] The roller shell 02 rotating on the fixedly clamped shaft 02 is driven by means of friction by another roller, not represented, for example an inking or dampening roller. The first gear wheel 13, which is seated freely rotatable on the eccentric section 47 of the shaft 06, meshes with the interior tooth arrangement 17 of the second gear wheel 18. Because of a difference in the number of teeth, for example 60 to 66, the first gear wheel 13 is provided with a greater number of revolutions n₁ in comparison with a number of revolutions n₂ of the roller shell 02 with the second gear wheel 18.

[0024] The obliquely arranged drive element 33, which supports the inner race 34, is rotated via the coupling 26. The lift frequency corresponds to the speed difference generated by the two gear wheels 13, 18.

[0025] Because of the radial displaceability of the ball socket of the joint 44 on the outer race 38 it is possible to change the lift length h of the roller shell 02, for example shorten it.

[0026] The coupling 26 exerts a compensating effect between the eccentrically seated stud bolts 20 to 23, the circumference of each of which rolls off on the inner wall of the bores 27 to 30. The bores 27 to 30 are arranged centered in respect to the axis of rotation 12.

[0027] In connection with this, a respectively first position of the stud bolts 20 to 23 and bores 27 to 30, and a dashed second position after a rotation by 450, are represented in FIG. 3. The ball bearing 32, the sleeve 48, as well as the roller shell 02 are not represented in the sectional representation in accordance with FIG. 3.

[0028] In accordance with an embodiment variation of the invention it is provided that the gear 09 for generating a number of revolutions n₁ differing from the number of revolutions n₂ of the roller shell 02, as well as the means 36, 39 02 for generating the axial lift h can be designed as a compact axial insert into the roller shell 02. To this end a sleeve 48, fixed against relative rotation, is provided on the interior 16 of the roller shell 02.

[0029] It is furthermore also possible in an alternative way to flexibly connect the inner race 34 of the bearing 36 with the interior 16 of the roller shell 02. In that case the outer race 38 is stationarily arranged in relation to the axial direction A of the friction roller 01.

[0030] In accordance with another embodiment variation it is possible for the stud bolts 20 to 23 of the coupling to be made of an elastic material. However, the stud bolts 20 to 23 have at least an elastic cover without changing their diameter d.

[0031] It is of course also possible to coat the interior of the bores 27 to 30, which are in engagement with the stud bolts 20 to 23, with an elastic material. In that case the diameter D of the bores 27 to 30 is preserved.

LIST OF REFERENCE SYMBOLS

[0032] 01 Roller

[0033] 02 Roller shell (01)

[0034] 03 Flange (01)

[0035] 04 Bore (03)

[0036] 05—

[0037] 06 Shaft (01)

[0038] 07 Rolling bearing

[0039] 08 Inner race (07)

[0040] 09 Gear

[0041] 10—

[0042] 11 Roller bearing

[0043] 12 Axis of rotation (01)

[0044] 13 Gear wheel, first (09)

[0045] 14 Exterior tooth arrangement (13)

[0046] 15—

[0047] 16 Interior

[0048] 17 Interior tooth arrangement (18)

[0049] 18 Gear wheel, second (09)

[0050] 19—

[0051] 20 Stud bolt (18)

[0052] 21 Stud bolt (18)

[0053] 22 Stud bolt (18)

[0054] 23 Stud bolt (18)

[0055] 24 Axis of rotation (13)

[0056] 25—

[0057] 26 Coupling

[0058] 27 Bore

[0059] 28 Bore

[0060] 29 Bore

[0061] 30 Bore

[0062] 31—

[0063] 32 Ball bearing (33)

[0064] 33 Drive element (34)

[0065] 34 Inner race (36)

[0066] 35—

[0067] 36 Ball bearing

[0068] 37 Axis of rotation (36)

[0069] 38 Outer race (36)

[0070] 39 Joint (38, 16)

[0071] 40—

[0072] 41 Connecting rod (39)

[0073] 42 End (39)

[0074] 43 End (39)

[0075] 44 Joint, first (38)

[0076] 45—

[0077] 46 Joint, second (16)

[0078] 47 Section, eccentric (06)

[0079] 48 Sleeve (16)

[0080] A Direction of lift, axial (01)

[0081] D Diameter (27 to 30)

[0082] d Diameter (20 to 23)

[0083] e Amount of eccentricity

[0084] h Lift length, axially (02)

[0085] n1 Number of revolutions (13)

[0086] n2 Number of revolutions (02, 18)

[0087] α Angle 

1. A roller with an axial lift (h), characterized in that for generating the lift (h) a bearing (36), which is obliquely arranged at an angle (α) in respect to the axis of rotation (12) of the roller (08), is arranged in the interior of the roller (01), wherein one of the races (34, 38) of the bearing (36) is stationary in respect to the axial direction of the roller (01), and the other race (38, 34) is connected with the roller shell (02).
 2. The roller in accordance with claim 1, characterized in that a force takeoff point (44) can be radially displaced toward the roller shell (02) of the bearing (36) for changing the lift.
 3. The roller in accordance with claim 1, characterized in that the two races (34, 38) have a different number of revolutions (n₁-n₂), and that this different number of revolutions (n₁-n₂) is unequal to the number of revolutions (n₂) of the roller shell (2).
 4. The roller in accordance with claim 1, characterized in that the outer race (38), viewed in relation to the axial direction (A) of the roller (01), is stationary, that the inner race (34) is flexibly connected with the roller shell (02).
 5. The roller in accordance with claim 1, characterized in that the inner race (34), viewed in relation to the axial direction (A) of the roller (01), is stationary, that the outer race (38) is flexibly connected with the roller shell (02).
 6. The roller in accordance with claim 1, characterized in that the bearing (36) is embodied as a roller bearing.
 7. The roller in accordance with claim 1, characterized in that an axis of rotation (37) of the bearing (36) extends at an acute angle (α) of 5° to 15° in respect to an axis of rotation (12) of the roller (01).
 8. The roller in accordance with claim 1, characterized in that a flexible connection is arranged between the outer race (38) and the roller shell (02, 16), which consist of a connecting rod (41), each of whose ends (42, 43) is designed as a joint (44, 46).
 9. The roller in accordance with claim 8, characterized in that a ball socket of the joint (44) is arranged on the outer race (38) of the bearing (36), and a ball socket of the joint (46) on the roller shell interior (16) of the roller (01).
 10. The roller in accordance with claim 8, characterized in that the ball socket of the joint (44), which is arranged on the outer race (38) of the bearing (36), is displaceably fastened for the purpose of changing the lift length in the direction toward the axis of rotation (37) of the bearing (36).
 11. A roller with an axial lift (h), wherein a coupling (26) is arranged between a centrally rotating element (33) and an eccentrically rotating element (13, 14), characterized in that a first rotating element (13) seated on a first axis of rotation (24) has at least two catches (20, 22, or 21, 23) pointing in the axial direction, which enter into a bore (27, 28, 29, or 30) of a larger diameter (D), wherein the bores (27, 29, or 28, 30) are located in a second rotating element (18), whose axis of rotation (12) extends axis-parallel and at a distance (e) to the axis of rotation (24) of the first rotating element (13), and that the eccentrically rotating element (13) has an exterior tooth arrangement (14).
 12. The roller in accordance with claim 11, characterized in that a first element of the coupling (26) consists of a first gear wheel (13) of a gear (09), which is eccentrically seated on a shaft (06, 47) of a roller (01) and whose exterior tooth arrangement (14) meshes with an interior tooth arrangement (17) of a second gear wheel (18) of the gear (09), which is fixedly arranged on the roller shell interior (16), that the first gear wheel (13) has on its flank at least one stud bolt (20, 21, 22, or 23) pointing in an axis-parallel direction of the roller (01), which respectively enters into a bore (27, 28, 29, or 30) of a second element of the coupling (26) seated on the shaft (06).
 13. The roller in accordance with claim 11, characterized in that the second element of the coupling (26) consists of a drive element (33) seated on the shaft (06) by means of a bearing (32) as the support of an inner race (34) of the obliquely arranged bearing (36).
 14. The roller in accordance with claim 12, characterized in that several stud bolts (20 to 23) of the first coupling element act together with several bores (27 to 30) of the second coupling element.
 15. The roller in accordance with claim 12, characterized in that the diameter (D) of each bore (27 to 30) at least corresponds to the diameter (d) of each stud bolt (20 to 23), plus twice the amount of the eccentricity (e) of an element (47) of the shaft (06) of the roller (01).
 16. The roller in accordance with claims 1 or 11, characterized in that a gear (09) for generating a number of revolutions (n₁) which differs from the number of revolutions (n₂) of the roller shell (02), as well as the means for generating the axial lift (h), can be embodied as a compact axial insert into the roller shell (02, 48).
 17. The roller in accordance with claims 1 or 11, characterized in that the roller (01) is embodied as an ink unit roller of a rotary printing press. 